Package control mechanism for winding machines



March 1963 P. L BARNES, JR, ETAL 3,031,046

PACKAGE CONTROL MECHANISM FOR WINDING MACHINES Filed May 19. 1960 c 4 Sheets-Sheet 1 ATTORNEY March 12, 1963 P. l. BARNES, JR., ETAL 3,031,046

PACKAGE CONTROL MECHANISM FOR WINDING MACHINES Filed May 19, 1960 I, 4 Sheets-Sheet 2 Z/ if? #4 ATTORNEY March 12, 1963 P. l. BARNES, JR., ETAL 3,031,046

' PACKAGE CONTROL MECHANISM FOR WINDING MACHINES 4 Sheets-Sheet 3' Filed May 19, 1960 o 1 Hll lii '/////7/ ATTORNEY March 1963 P. BARNES, JR., ETAL 3,081,046

PACKAGE CONTROL MECHANISM FOR WINDING MACHINES Filed May 19, 1960 4 Sheets-Sheet 4 M E. R'r'FYE l, ,2 Til gig/,5:

ATTORNEY 3,081,046 PACKAGE CONTROL MECHANISM FOR WINDING MACHINES Porter I. Barnes, Jr., Johnston, and Thomas E. Pitts,

Cranston, R.I., assignors to Leesona Corporation,

Cranston, R.I., a corporation of Massachusetts Eiled, May 19, 1960, Ser. No. 30,347 19 Claims. (Cl. 242-36) This invention relates to a control mechanism for the delivery package of a Winding machine and is more particularly concerned with a mechanism for latching the delivery package of a winding machine in winding position and for releasing the package from that position upon the occurrence of any one of a plurality of conditions.

In US. Patent 2,764,362 to Goodhue et al., entitled, Winding Machines, issued September 25, 1956, there is disclosed and claimed a fully automatic winding machine for winding yarn or the like into various forms of packages, especially cones.

In essence, the machine of this patent consists of a winding section including a rotatable winding mandrel mounted for controlled movement between a winding position, a braking position, and a reverse rotation position and a drive roll for rotating the package in winding position and provided with a groove to traverse the yarn being wound upon the package; an end-finding and reuniting section operable in the event of thread breakage, which section includes a knotter and separate means for finding the respective free ends of the broken yarn and conveying them to the knotter to be joined together; a preliminary yarn servicing section including means for detecting, tensioning, and cleaning the yarn supplied to the mandrel; and an enclosed control section for superintending the other sections and controlling the functioning thereof. It was contemplated in this machine that the winding mandrel was carried by a main package arm mounted for pivotal movement on one side of the control section adjacent the rear end thereof, the arm being moved by means of a control cam. The control cam was provided with an arrangement of consecutive camming surfaces operable during rotation thereof to move the arm from a normal winding position to a braking position, with a sufficient dwell at the braking position to allow the rotating package to be brought to a halt, and then to a reverse rotation position, where the package was rotated in a direction opposite to that of normal winding to enable the free end of a broken thread to be extricated from the convolutions on the package, engaged by a delivery end-finding means and conveyed to the knotter for connection to the free supply end, the dwell at reverse rotation position being sutficient for the end-finding means to perform its function. After this dwell at the reverse rotation position, during which the cam continued to rotate, the main package arm was moved by the cam in the opposite direction to bring the package first to braking position to halt its reverse rotation, at which time the ends were re-united, and then to normal winding position and into peripheral contact with the drive roll.

Rotation of the package control cam to move the main package through the stages just described was instigated as a result of thread breakage and, when the thread was running properly, the cam was locked against rotation, the main package arm being held in normal winding position by the corresponding camming surface on the control cam.

While it is virtually essential for the package to be moved between these several positions during the endfinding and re-uniting cycle of the machine, this is not the only time at which movement of the package away from normal winding position is desirable. For exam- United States Patent 3,081 ,046 Patented Mar; 12, 1963 ple, when the package has grown to the desired ultimate size, prevention of the winding of additional yarn thereon is obviously important. Since the package drive roll was constantly rotating in the patented machine, this could be achieved only by moving the package away from the roll. However, as already explained, the main package arm was very effectively restrained against movement by the arm control cam, and to resort to a rather complicated lift mechanism acting on a package arm extension was necessary in order to disengage the package from the drive roll.

Again, the traveling yarn may accidentally become attracted to the drive roll and wind therearound instead of upon the package, forming what is known in the art as roll lap, which can build up to such an extent between two rigidly mounted adjacent parts as to exert sufiicient force to actually bend one of those parts. The patented machine lacked a device for sensing the build-up of a roll lap and, due to the inability of the main package arm to pivot to lift the package away from the constantly rotating drive roll, the addition to that machine of a knock-off motion effective to halt the delivery of the yarn and to disengage the package from the roll would be most difiicult, except through the utilization of a complicated arrangement similar to the lift mechanism already described.

From these considerations, it will immediately be apparent that the direct relationship between the main package arm and the package arm control cam, whereby the position of the former was determined exclusively by the latter, constituted a rather serious practical defect in the design of the patented machine; and a principal object of the present invention is to divorce from the control cam operable during the end-finding and reuniting cycle, the function of maintaining the main pack-. age arm and the package carried thereon in operative position during normal winding, while still allowing that cam to govern the position of the main package arm and package during the end-finding and re-uniting cycle.

A further object of the invention is a main package arm latch operative to maintain the main package arm in normal winding position, which latch is wholly independent of the main package arm control cam and is adapted to be disengaged from the main package arm to permit the arm to move the package away from the drive roll in the event of either of breakage of the thread, the occurrence of a roll lap, or the attainment of ultimate package size.

Another object of the invention is to provide the winding machine with a main package arm capable of limited movement independently of the package control cam to disengage the package from the package drive roll, such movement of the main package arm being eifective to sever the yarn being delivered to the package, except when thread breakage occurs and an end-finding and re-uniting cycle is institute-d.

An additional object of the invention is a winding machine including a latch for positioning the main package arm in operative position for normal winding independently of the main package arm control cam, which latch is disengaged prior to the beginning of an end-finding and reuniting cycle to permit the package to move to braking position immediately and in advance of the rotation of the control cam.

In the course of re-designing the control section of the machine to achieve the above objectives, it was found possible to effect a major simplification in the mechanism for bringing the winding operation to a halt when the package had achieved the desired ultimate size and, accordingly, the present invention also embodies novel features in the package sizing mechanism.

Thus, another object of the invention is the provision of a package sizing latch operatively associated with the main package arm positioning latch for automatically disengaging the positioning latch at the moment the desired ultimate package size is attained, whereby the main package arm and the package carried thereby are released from normal winding position to remove the package from driving contact with the package drive roll and to sever the yarn being delivered to the package.

A further object of the invention is a winding machine including a package sizing latch of the type just described, which, after releasing the main package arm from the package arm positioning latch to permit the main package arm and package to move away from winding position, is effective to stop the arm and package in a position intermediate normal winding and braking positions, whereby the package remains in an essentially forward location and is readily accessible to the machine attendant.

A still further object of the invention is the provision of a package sizing latch of the type described which is easily adjustable to permit the size of the ultimate package to be varied.

These and other objects and advantages of the present invention will be apparent from the following detailed description when read in conjunction with the accompanying drawings, in which:

FIG. 1 is a right side elevation of the control section of the winding machine of U.S. Patent 2,764,362 embodying the improvements of the present invention, the components of the section being shown in normal winding position;

FIG. 2 is a view similar to FIG. 1, but with the components shown in the position assumed thereby when the package has achieved the desired ultimate size and the winding operation is halted;

FIG. 3 is a top plan view, looking down on the control section of the machine, certain of the elements normally in this section being omitted for sake of clarity;

FIG. 4 is a detailed view, partly in elevation and partly in section, showing the operating means for the yarn severing means and also certain elements of the locking means for the control cam unit;

FIG. 5 is an enlarged detailed view of the yarn severing means of FIG. 4 in the position assumed thereby when the yarn is severed;

FIG. 6 is an enlarged detailed view of the cam unit locking means of FIG. 4, with the end severing means and its associated operating means omitted, the locking means being shown in disengaged position;

REG. 7 is a view similar to FIG. 6, but with the cam unit locking means shown in engaged position; and

FIG. 8 is a view similar to FIG. 2, showing the package positioning and supporting components in the position assumed after either thread breakage or roll lap has occurred.

Before proceeding with the detailed description of the invention, it should perhaps be explained that the improvements of the present invention are essentially confined to the winding section and control section of the winding machine of the previously identified patent. As the other sections of the machine form no part of the invention, they will neither be described nor illustrated here. Similarly, some of the elements normally forming a part of the control section of the patented machine have no real relationship to the details of the invention and have likewise been omitted. Thus, for an over-all understanding of a complete operating machine, reference should be made to the aforesaid Patent 2,764,362. It will be understood that the parts of the patented machine which are absent from this description and the accompanying drawings will ordinarily be present in a complete working machine and may be the same as shown and described in that patent.

Turning now to a detailed description of the drawings, with initial reference to FIGS. 1 and 3, the numeral 20 designates a U-shaped frame for the control section of the winding machine, which frame comprises a generally rectangular base 21 and side-walls 22 and 23 upstanding from opposite side edges of the base. Located above frame 20 adjacent the front thereof is a package drive roll D and a reverse rotation roll R, the means for supporting and driving these two rolls being omitted, and a braking member B arranged between rolls D and R and supported by means which will be described later. Braking member B may be in the form either of an elongated cylindrical rod, as shown in FIG. 1, or a fiat plate, as shown in the aforesaid patent. Drive roll D, braking member B, and reverse rotation roll R constitute three of the four positions assumed by the package during the operation of the machine (the fourth position being seen in FIG. 2) and in FIG. 1, the package being wound is shown in the first of these positions, namely, in frictional contact with the periphery of roll D. The normal position of the package, when winding, proceeds in a regular manner.

As illustrated, the machine is set up to wind a conical package or cop upon a conical paper tube or core held on a winding mandrel or cop holder 24, which is likewise conical, although other shapes of mandrels and tube could be substituted. Winding mandrel 24 is rotatably mounted on a winding spindle (not visible in the drawings) which is, in turn, supported on a generally transversely extending arm (also not visible in the drawings) capable of pivotal movement at its end about a substantially vertical axis. The end of this arm is fitted within a socket 26 provided for that purpose at the free end of an extension arm 28 disposed in approximate vertical alignment with frame side 22. The end of extension arm 28 opposite socket 26 is rotatably held in two spaced-apart bearing collars 30 and 32 formed as an integral part of an irregularly shaped joint member 34. At its lower end, member 34 is pivoted on a stud shaft 36 extending horizontally and inwardly of the upper end of a massively constructed, elongated link 38, which is herein designated the main package support arm. It will be seen that, in effect, joint member 34 functions as a kind of universal joint permitting package extension arm 28 to pivot with respect to both the horizontal axis of stud shaft 36 and the upwardly and forwardly inclined axis of spaced-apart bearings 30, 32, whereby the winding spindle and mandrel can swing upwardly as a unit about shaft 36 away from drive roll D, as well as to pivot backwardly and forwardly with respect to socket 26 and to cant upwardly with respect to bearings 30, 32. In this way, the winding spindle is adapted to recede from the driving roll in a manner suitable for the building of a conically shaped package.

Main package arm 38 is pivoted at its lower end adjacent the upper rear corner of frame side 22 on the exterior end of a shaft 40 extending transversely the full width of frame 29 and journaled in suitable hearings in the frame sides (FIG. 3). Located adjacent the upper edge of frame side 22 intermediate the ends thereof is an outwardly projecting stud 4-2 on which is pivoted an elongated plate 44 extending parallel to side 22 and adjacent the inside face of arm 38, which plate constitutes the main package arm positioning latch, termed for con- 1 venience the main package latch or simply main latch.

At its extreme rear end, main latch 44 terminates in a downwardly curved tail 46, for a purpose to be described later. Slightly forwardly of tail 46, the upper edge thereof is formed with a shoulder 48 adapted to be engaged by a pin 59 rigidly embedded in main package arm 38 at a point thereon somewhat closer to stud shaft 36 than to shaft 40. Pin 59 projects a short distance inwardly of arm 38, the adjacent portions of the arm being cut away i in FIG. 1 to show pin 50 in section, and the rear face of the pin is preferably flattened for better engagement with shoulder 48. Also, on the upper edge of the main package latch, at a point spaced forwardly and slightly above the level of shoulder '48, is a second shoulder 52 whose function will be described in connection with the package sizing mechanism.

The portion of main latch 44 forwardly of pivot stud 42, i.e., to the left of that stud in FIG. 1, is provided with two spaced-apart clamping bolts 53, which clampingly engage the foot portion 54 of a generally upwardly projecting support arm 56, the lower edge of foot portion 54 being correspondingly slotted, as at 58, to slip over bolts 53 when loosened. The free upper end of support arm 56 rigidly holds the outer end of package braking memher B. Below the front end of the foot portion 54 of the braking member support, the main package latch is connected to one end of a tension spring 60 having its other end fastened on a post 62 projecting laterally on the outside of frame side 22. Spring 60 exerts constant counterclockwise bias on main latch 44 to urge the rear end thereof upwardly into engagement with pin 50 on main package support arm 38. The extreme forward end of main latch 44 is pivotally joined to the upper end of a downwardly extending link 64 having-its lower end connected to a pivot pin '66 by a slot 68 which is elongated downwardly to afford a certain amount of lost motion to pin 66 in that direction. Pin 66 is carried at the end of a crank 70 fixed to the exterior end of a shaft 72 for rotation therewith.

From the mechanism thus far described, it will be seen that, assuming the components are in normal operating position as shown in FIG. 1 with shoulder 48 on main latch 44 being engaged by pin 50 on main package support arm 38 to hold the arm in forward position with package P in frictional contact with drive roll D, if a rearwardly directed force is exerted on braking member B, main latch 44 will be pivoted clockwise to disengage shoulder 48 from pin 50, freeing main package support arm 38 for rearward pivotal movement. Braking member B is positioned in close proximity, say inch, to the peripheral surface of drive roll D and will, therefore, be contacted in the event the yarn being delivered to the package should accidentally become lapped around roll D. Thus, braking member, in addition to functiomng to brake the package, serves as the roll lap detector, being forced to the rear away from the periphery of roll D in the event of a roll lap to disengage main package support arm 38 and allow the package to fall backwardly to a position resting upon the braking member (shown in FIG. 8) and out of driving engagement with drive roll D. By virtue of the lost motion connection between slot 68 on link 64, and pin 66 on crank 70, main latch 44 is free to pivot clockwise the necessary distance away from pin 50 without affecting crank arm 70.

1 As already explained in the introduction, one ofthe important features of the present invention is the ability of main package arm 38 to retrogress almost immediately in the event of thread breakage without waiting for the beginning of an end-finding cycle. To fully comprehend this feature, it is necessary that the difference in the relationship of the main package support arm and the control cam for that arm between the patented machine and the present invention be appreciated. I

Main package support arm 38, as already stated, mounted on the exterior end of a rotatable shaft 40 extending between the frame sides. Carried on shaft 40 for rotation therewith adjacent side 2 is a collar or hub 76 (see FIG. 3) formed with an integral downwardly and forwardly curved follower leg 78 having a follower roller 80 at its free ends. Roller 80 is adapted to engage the peripheral edge of a plate cam 82, termed the main package control cam, which forms a part of the control cam unit of the machine. Cam 82 includes a salient portion 84 for moving main package arm 38 and package to normal winding position, two portions 86 of intermediate radius, one on either side of salient portion 84, for moving the main package arm to braking position, both before and after the arm is moved to normal wiiiding position, and a portion 88 of minimum radius opposite salient portion 84 for moving the arm and package to reverse rotation position. The control cam unit of the machine, including package control cam 82, is fixed on a main control shaft 90 for rotation therewith, and it will be seen that as shaft 90 rotates, the main package arm will be moved by the peripheral portions of control cam 82 in a cycle between the three operating positions.

In accordance with the patented machine, the maximum radius salient portion was extended circumferentially in the direction opposite to the direction of cam rotation a somewhat greater extent than is the case with the corresponding portion of the present cam, with the result that the salient portion of the previous cam remained in engagement with follower roller 80, 'while the main package arm and the package were in normal winding position.

.t should perhaps be explained that, after rotation to bring the salient portion into engagement with the main package arm follower to shift the main package arm and package to normal winding position, shaft 90 was restrained against further rotation until the initiation of a further end-finding cycle. The same is true of the present arrangement, except that, once the main package arm has been brought to normal winding position by salient portion 84, it is now latched or locked in that position by engagement of pin 50 with shoulder 48, on main latch 44, and further rotation of shaft 90, to the position to which it is checked at the finish of an end-finding cycle, carries salient portion 84 out from under roller 80, whereby roller and follower arm 78 are free to move inwardly towards shaft until contact is made with the trailing intermediate radius cam portion 86. Thus, salient portion 84 no longer serves as the keeper for the main package arm in normal winding position, this function being exercised instead by main latch 44.

An understanding of the actuation of main latch 44 in response to breakage of the thread requires a discussion of the thread breakage-lever and the control shaft locking means, which are best shown in FIGS. 3, 4, 6 and 7. Breakage-lever takes the form of a generally L-shaped .rod having its foot portion 102 extending in spaced parallel relation to the forward end of frame 20 across and at right angles to the path of the yarn and its leg portion 104 extending rearwardly alongside frame side 23. At its rear end, leg portion 104 of the breakage lever is affixed to a connecting plate 106 (FIG. 3) pivoted on a shaft 108 and extended rearwardly of that shaft to assist in counter-balancing the breakage-lever. In normal running position, breakage-lever is maintained in a depressed position (as in FIG. 1) by the thread passing thereover, but, in the event of thread breakage, will tilt upwardly about the axis of shaft 108, the balance of the breakage-lever being selected to cause such tilting movement.

Shaft 108 passes through a bearing in frame side 23 to about the mid-point of the housing and is supported at its inner end -in a bearing provided in an intermediate partition wall 110 rigidly upstanding from frame base 21. Afiixed on shaft 108 for rotation therewith intermediate partition wall 110 and side 23 is a generally Y-shaped breakage-lever yoke 112 having two rearwardly extending arms, only one of which (114) is shown in the drawings, one forwardly extending arm 116, and a common hub 1'18 axially bored to receive shaft 108. The breakage-lever and the breakage-lever yoke, therefore, pivot with shaft 108, downward movement of the breakagelever being limited by engagement of the upper edge of rear arm 114 with a tubular brace stretching between frame side 23 and partition wall 110 and connected at its ends thereto adjacent the upper edges thereof. Freely dangling from a stud 122 on the rear end of yoke arm 114 is a pawl 124, herein referred to as the package-lifting pendant, which is adapted, under certain conditions, to engage a convex rear edge at the upper end of a generally vertical latch lever 126 to rock that lever forwardly about a horizontal shaft 128 supported at its ends in frame side 23 and partition wall 116 a considerable distance below brace 12%. Adjacent its forward edge, the upper end of latch lever 126 is pivoted to a forwardly extending connecting link 130, the other end of which is pivoted to the upper end of a normally upstanding crank 132 fixedly carried on the inner end of shaft 72.

Shaft 72 is supported in bearings in partition 118 and frame side 22 at a level spaced downwardly and forwardly of breakage-lever shaft 168 and is biased in a clockwise direction (FIG. 6) by means of a torsion spring 134 (see FIG. 3), encircling a portion of the shaft adjacent frame side 22, one of the ends of spring v134 being embedded in that side and the other anchored on a collar 136 firmly secured to shaft 72 by means of a set screw 38. It will be recalled from the discussion of FIG. 1 that shaft 72 carries on its exterior end a normally horizontally extending crank 70 which is connected through pin 66 and slotted link 64 to the front end of main latch 44. It will now be seen that forward rocking motion of latch lever 126 will impart a corresponding movement to shaft 72 and exterior crank 7 0, forcing the front end of main package positioning latch 44 upwardly to lower the rear end thereof and disengage shoulder 48 from pin 58 on the main package support arm. As before, when shoulder 48 is disengaged from pin 50, the main package arm is free to swing rearwardly until follower roller 80 on package arm follower leg 78 engages the trailing intermediate radius portion 86 of package arm control cam 82, positioning package P with its periphery in frictional contact with braking member B.

The conditions, or more precisely, the condition under which breakage-lever pendant 124 engages latch lever 126 to rock shaft 72 is closely interrelated with the drive for the main control shaft 90 of the control section. For simplification, the main driving element for shaft tl may be deemed to be a notched disc plate 140 (see FIGS. 4 and 6) which is arranged for free rotation on shaft 96 around a bushing 142, plate 148 being termed herein as the drive plate for shaft 90. For the purposes of this invention, it is enough to know that drive plate 148 is constantly driven at a suitably selected speed, the driving means for that plate forming no part of the invention and being explained in the aforementioned Goodhue et al. patent. In essence, however, drive plate 149 is driven through a friction clutch comprising a circular plate 144 (see FIG. 3) rigidly coupled to plate 140 and frictionally engaged by means (not shown) yieldably supported within a cylindrical housing 1 .6 having an integrally formed peripheral gear 148 which is, in turn, driven by a gear train (not shown) deriving power from the main drive shaft (also not shown) of the machine. Mounted on drive plate 140 is a plurality of laterally projecting pins 158 located at equally spaced points therearound on a common radius.

When the thread breaks, or is broken, during the winding operation, breakage-lever 108 swings upwardly to rock breakage-lever shaft 108 and breakage-lever yoke 112 downwardly to the position shown in FIG. 7, thrusting breakage-lever pendant 124 into the space between plate 140 and clutch plate 144 to a position at which the pendant will intrude between the moving pins 156 and the rear edge at the upper end of latch lever 126. As can be seen in FIG. 6, the radius of pins 150 on plate 140 is so selected that insufficient clearance exists between the upper rear edge of latch lever 126 and a pin 150, when proximate to that edge, to accommodate pendant 124. Consequently, as an oncoming pin engages breakage-lever pendant 124 the pendant will be swung forwardly about its pivot 122 to permit the pin to pass, and latch lever 126 will likewise be swung forwardly with the result that shaft 8. 72 will be rocked in a counterclockwise direction in FIG. 6, this motion being transmitted to main package positioning latch 44 to unlatch the main package arm.

The arrangement by which drive plate 140 is coupled to shaft will now be described. Fixed on shaft 90 at a location spaced slightly from drive plate in a direction toward the observer in FIG. 6 is an actuator disc 154 which bears a pivot pin 156 at a point spaced slightly inwardly of its periphery, and pivoted on pin 156 between actuator disc 154 and drive plate 140 is an inverted L- shaped driver-pawl 158. Intermediate pivot axis 156, on the forward edge of driver-pawl 153, and its lower end is a laterally directed lug 16ft adapted to engage with one of the notches 162 provided at equally spaced points around the periphery of drive plate 140. The lower end of driver-pawl 158 is connected to one end of a tension spring 164, the other end of which is anchored on a post 166 on actuator disc 154, so that spring 164 urges driver-pawl 158 in a counterclockwise direction about pin 156. Thus, when driver-pawl 158 is free to rotate, it will be urged inwardly by spring 164 into engagement with one of the notches 162 on driver plate 140 to couple that plate to actuator disc 154 for simultaneous rotation.

In order to hold lug on driver-pawl 158 out of engagement with a peripheral notch on the drive plate, the upper end of driver-pawl 158 includes an outwardly projecting beak 167 having a straight, lower edge 168 which is adapted to engage a detent shoulder 170 at the upper end of a laterally directed flange 172 on latch lever 126. In approximately the same radial plane as the axis of pivot pin 156, the peripheral edge of actuator disc 154 is formed with a radial shoulder 174, the remainder of the disc periphery being substantially circular in configuration. Shoulder 174 is also adapted to engage shoulder 170 at the upper edge of flange 172. It will be seen that as long as edge 168 on driver-pawl 158 and radial shoulder 174 on actuator disc 154 are in contact with shoulder 170 on the latch lever (the position shown in FIG. 6), the lug of the driver-pawl will be held away from the periphery of drive plate 14% to uncouple actuator disc 154 therefrom and disc 154 will be restrained against rotation by the engagement of shoulder 174 on the cooperating latch lever shoulder 170. However, when latch lever 126 is forced forwardly in the manner already explained, detent shoulder 170 of the latch lever will be moved out from beneath radial shoulder 174 on actuator disc 150, as well as the edge 168 of driver-pawl beak 167, releasing the actuator disc for rotation and allowing driver-pawl 158 to pivot under the influence of spring 164 about its pivot pin 156 to engage driver-pawl lug 160 with the first notch 162 on driver plate 140 that approaches the lug. As soon as the lug is engaged with a notch, actuator disc 154 and drive plate 140 are coupled and rotate as a unit. Only one revolution of such uni tary rotation will occur, however. This follows from the fact, that as driver-pawl 158 swings inwardly to couple the disc and plate together, edge 168 on the driver-pawl beak will be projected in leading relationship to radial shoulder 174 on the actuator disc (FIG. 7), so that as the revolution is completed, edge 168 will contact the latch lever 170 slightly in advance of radial shoulder 174.

When this occurs, actuator disc 154, being still coupled to drive plate 140, will continue to rotate to bring its radial shoulder 174 into engagement with the latch lever shoulder, since the latch lever is subject to a constant inward bias from spring 134 through shaft 72, crank 132 and link 130. Driver-pawl shoulder 168, however, is no longer free to move and relative rotation between the driver-pawl and actuator disc must take place, disengaging the driver-pawl lug from the peripheral notch of the drive plate, stopping the rotation of the actuator disc with the parts back in rest position, as shown in FIG. 6.

To prevent backward rotation of the actuator disc as radial shoulder 174 engages shoulder 170, an arm 169,

which is pivoted on shaft 40, carries a cam follower 1711 for engagement with a second cam 173 on control shaft 90, arm 169 being biased upwardly against the periphery of cam 173. Cam 173 includes on inclined peripheral portion 175 at a point suitable for engagement with follower 171 when the two shoulders approach contact, the inclination of portion 175 being such as to oppose, under the bias of follower 171, clockwise rotation of the cam and disc. In addition, when the actuator disc is released, inclined portion 175 tends to initiate the rotation of the disc to eliminate any possibility of the shoulders reengaging before the drive-pawl is effectively released.

Package arm control cam 82, along with a plurality of additional cams, including cam 173, seen between cam 82 and actuator disc 154 in FIG. 3, is formed as a unitary cam assembly, preferably constructed of' plastic, such as nylon, or the like, and the entire assembly is secured to main control shaft 90 for rotation therewith. These additional cams play various roles during the end-finding cycle of the machine, their specific function having no essential bearing on the present invention and being explained in the aforementioned Goodhue et al. patent. It is obviously desirable for the machine to be capable of winding various size packages and for terminating the winding operation once the particular package size contemplated has been achieved. The mechanism by which these ends are achieved will be described next, with particular reference to FIGS. 1 and 2. Mounted on stud shaft 36 between the upper end of main package support arm 38 and the outer face of joint member 34, for pivotal movement with respect to that shaft is a package-sizing lever plate 180 of highly irregular configuration. At the lower rear end of lever 180 is a generally downwardly directed tail portion -182 terminating in an outwardly directed lu-g 184 and along the lower edge of lever 180 slightly forwardly of tail portion 182 is an elongated, outwardly rolled lug 185 extending to about the mid-point ofthat lower edge to present an elongated, downwardly facing peripheral surface 186. An arm portion 188 stretches forwardly from the lower front corner of lever 180, by means of which the lever may be manipulated, and upwardly and inwardly of arm portion 188' is a generally vertical, slightly curved, elongated slot 190. Slot 190 is penetrated by a threaded bolt 192 fixed on joint member 34, a nut 194 being threaded on the exterior end of bolt 192 to clamp lever 180 relative to joint member 34 in any position within the limits of slot 190.

i i Cooperating with sizing lever .180 is a sizing latch 196 pivoted at approximately its mid-point on a pin 198 rigidly embedded in the inner face of main package sup port arm 38. Sizing latch 196 is of roughly Y-shaped configuration having a rearwardly directed tail portion 200 and two forwardly and somewhat downwardly directed arms 20.2 and 204. Adjacent the rear end of the upper edge of tail portion 200 is a vertical shoulder 206. From shoulder 206 rearwardly, the upper edge of tail 200 is downwardly inclined, as at 208, and the adjacent lower edge portion is preferably upwardly and rearwardly inclined, at at 210, so that the tail terminates in the shape of a V. The foremost arm 202 of the two arms of sizing latch 196 terminates in an inwardly bent lug 212..

Preparatory to the Winding operation, bolt 194 is loosened and arm 188 manipulated to position the sizing lever in accordance with the size of the package which is to be wound, the forward face of joint member 34 being provided with a scale, indicated at 21 4, for gauging the package size, after which bolt 194 is tightened to clamp the sizing lever to the joint member so that they rotate as a unit about stud shaft 36 as the package grows in size. The downwardly facing peripheral surface 186 on the sizing lever is of suflicient length that when the package arm extension 28 is in downward position, as would inevitably be the case at the start of the winding operation, the tip of shoulder 206 on the sizing latch tail portion will contact surface 186 irrespective of the size of the package for which the sizing lever is set, entry of the shoulder tip onto surface 186 as package extension arm 28 is lifted upwardly, as during a mandrel changeover, or the like, being facilitated by the inclination of upper edge 208 at the tail portion terminal. Latching lever 196 .is biased in a counterclockwise direction (in FIGS. 1 and 2) by a torsion spring 216 anchored on pivot pin 198, iwth one end seating against the upper face of lug 212 and the other against pin 50 on main package support arm 38, and the tip of shoulder 206 will, therefore, be urged against peripheral surface 186 on the sizing lever. As long as the shoulder tip and surface are in contact, lug 212 on the foremost arm of the latching lever will be held vertically spaced above the upper edge of main package positioning latch 44.

During the winding operation, package P will, of course, grow 'in size, pivoting extension arm as well as joint member 34 and sizing lever 180 about stud shaft 36, the shoulder tip riding all the while against surface 186, until the rear end of surface 186 passes the shoulder tip, freeing the tail of the latching lever for upward movement until the upper edge thereof forwardly of shoulder 206 meets surface 186. The upward motion of tail 206, aided by the thrust of spring 216, imparts a suificient downward motion to arm 202 as to cause its lug 212 to strike the upper edge of main package positioning latch 44, driving the main latch downwardly and disengaging shoulder 48 from pin 50. This enables the main package support the machine.

beyond that size indicated in FIG. 2, sizing lever arm to fall rearwardly under the weight of the package. However, lug 212 on forward arm 202 of the latching lever is now proximate to the upper edge of main latch 44 and will engage the foremost shoulder 52 on that lever as the main package arm falls rearwardly. This halts the rearward movement of the arm at a point on its path intermediate normal winding position and braking position with the package in repose at a similar intermediate position, which is sufiiciently close to the front end of the frame as to be readily accessible to the machine attendant for purposes of removal.

From what has been said above, it follows that growth of the package is discontinued when the tip of shoulder 206 coincides with the rear end of peripheral surface 186 on sizing lever 180 and that the actual size of the package at this time will be a function of the distance on surface 186 between the initial location of shoulder tip 206 and the rear edge of the surface. The ability of sizing lever 180 to be moved to a variety of positions corresponding to the desired range of package sizes has already been alluded to and the length of surface 186 from front to rear is so chosen as to accommodate the shoulder tip throughout all of its positions corresponding to the range of package sizes.

The arrangement of the sizing lever and cooperating sizing latch just described includes a built-in safety feature operable in 'the event the latch fails to actuate upon leaving the end of surface 186 in order to prevent the package from growing to a size that would damage If the package should continue to grow will continue to pivot with joint member 34 around stud shaft 36 and, ultimately, lug 184 on sizing lever tail 182 will engage the lower inclined edge 210 at the rear end of sizing latch tail 200, forcing tail 200 upwardly or counterclockwise around pivot pin 198 to disengage pin 50 from shoulder 48 in the same manner as before. For this purpose, the length of tail 182 in relation to the position of edge 210 on the sizing latch is such that lug 184 will engage that edge as package extension arm 26 swings upwardly before the maximum permissible limit of package sizes is exceeded.

During the course of an end-finding cycle, package P not only moves bodily into engagement with braking member B but into engagement with reverse rotation roll R as well, and the function of tail portion 46 on main package positioning latch 44 is to maintain pin 50 on the main package arm in engagement with the upper edge of the main latch when the main package arm is in maximum rearward position with package P in contact with reverse rotation roll R. The relationship of the co1nponents of the machine in this position is indicated in dotted lines in FIG. 8. The upper edge of tail 46 is roughly of inverted V-shape, with its ends lying substantially on the path followed by pin 50 as main package arm 38 swings to and from extreme rearward position and the apex of the V is disposed above that path so that as the pin approaches the apex, main latch 44 will be pivoted clockwise, lifting its front end and raising braking member B a slight extent to more easily engage the package. Tail 46 is constructed long enough that pin 59 remains on the upper edge of main latch 44 at all times.

When the package has reached the desired size, or a roll lap has built up on the drive roll, and the package has been moved as a result thereof away from the drive roll, the disadvantage in having the thread run uninterrupted will be apparent. In the first case, the package will continue to spin under its own momentum after movement to the intermediate package-sizing position and cause additional convolutions of yarn to be wound therearound, while, in the second case, the thread, unless severed, will continue to wrap around the drive roll even though the pack-age is no longer in engagement therewith. On the other hand, interruption of the yarn during the end-finding cycle is both unnecessary and undesirable since the thread is already broken and the operation of a cutter might tend to interfere with the reunion of the broken ends and the return of the yarn to running position. The machine of the invention is, therefore, equipped with means operable to sever the yarn under the first two conditions, but not under the third, which means is best seen in FIGS. 4 and 5.

Fixed on shaft 40, about mid-way between frame sides 22 and 23 (see FIG. 3), is a crank 220 connected at its upper end to the angularly extending upper end 222 of an operating link 224 shaped generally in the manner of a dogleg and disposed below the cam unit driving and component latching. Link 224 is guided by means of a pin 226 passing through a slot 228 formed in the horizontally extending front portion 23f) of link 224, slot 228 being upwardly and forwardly inclined to a slight extent, whereby link 224 will reciprocate in an essentially straight line path as crank 220 is rocked incidentally to the movement of main package arm 38. At its extreme front end, operating link 224 is formed with an upwardly projecting toe 232, the inner edge of which defines a shoulder 234. Reference has already been made, in connection with the description of the thread breakage-lever and the actuating thereby of the cam unit latch, to the existence of a front arm 116 on breakage-lever yoke 112. At its forward end,

arm 116 carries a pin 236 on which is pivoted a downwardly hanging pendant 238. The extreme lower end of pendant 238 is provided with a generally U-shaped extension 240, including a laterally bent lug 242, which lug is adapted to engage shoulder 234 on toe 232 of link 224. Projecting forwardly of the main body of pendant 238, at right angles to the length thereof, is a leg 244 reversely bent at its front end, as at 246, in the manner of a hook.

Extending between frame sides 22 and 23 and journaled therein is a shaft 250 located directly above the hook end 246 of pendant leg 244 and at a point on this shaft adjacent side wall 23 is mounted, for free swinging movement with respect thereto, a combination yoke and L-shaped lever 252. The upper or yoke portion 254 of lever 252 is bent in U-shape, with its arms penetrated by shaft 250. The lower L-shaped portion 256, formed as an extension of the outside arm of the yoke portion, i.e., the arm adjacent side 23, stretches downwardly and then forwardly to terminate outside the front of frame 2t), as at 253. At the lower end of the inside arm of the yoke portion 254 is an extension 260, of reduced transverse dimension, which is engaged within the hook end 246 of pendant leg 244. Lever 252 is biased forwardly against a stop 262 on the inside face of frame side 23 by means of a tension spring 264 anchored at one end to L-shaped portion 256 of lever 252, and at its other end to a post 266 on frame side 23 adjacent its front edge.

When the breakage-lever yoke 112 is in normal operating position (shown in FIG. 4), as would be the case when the thread was running properly, and holding the thread breakage-lever in depressed position, pendant 238 is suspended with lug 242 of its U-shaped extension 240 in engagement with shoulder 234 on the toe end of operating link 224. Hence, as shaft 40 rocks with main package arm 38, pendant 238 will be pulled rearwardly about its pivot pin 236 by operating link 224 and will, in turn, pull lever 252 rearwardly about its supporting shaft 250, swinging the exterior front end portion 258 of lever 252 rearwardly and downwardly to the position shown in FIG. 5. Lever end potrion 258 is connected by a link 270 to the operating arm 272 of a knife blade 274 suspended in a frame 276 for downward and rearward swinging move ment to bring its cutting edge into contact with a fixed anvil 277 and normally biased away from the anvil. The yarn Y, being delivered to the winding section, passes between the knife edge and anvil 277 and when link 270 is pulled downwardly, the knife swings against the anvil to sever the yarn. Frame 276 is mounted on a forward section 278, c.g., the yarn servicing section, of the machine.

In the event the yarn breaks to institute an end-finding cycle, the breakage-lever swings upwardly, rocking shaft 108 and breakage-lever yoke 112 counterclockwise from the position shown in FIG. 4 to the position shown in FIG. 7. This lifts pendant 238 to a level at which lug 242 on extension 240 is held clear of shoulder 234 on toe 232 of operating link 224. Consequently, as link 224 is pulled rearwardly as main package arm 38 swings away from normal running position, pendant lug 242 is not engaged by toe 232 and lever 252 is held by spring 264 in normal and knife blade 274 remains away from anvil 277, allowing the yarn to travel uninterrupted during the endfinding cycle.

It will therefore be seen that the yarn will be severed when the main package arm is unlatched and swings rearwardly as a result either of either of package-sizing, i.e., attainment of the proper size by the package, or rolllap but will not be severed when the package arm is unlatched and swings rearwardly as a result of thread breakage. In view of the rather limited movement of main package arm 38 when package-sizing takes place, moving the package only part of the way to breaking position, the effective leverage of the several levers of the yarnsevering mechanism must be such as to operate the knife with this limited movement.

Yarn knife 274 and frame 276 may, and preferably do, form a part of a slub catcher for the yarn, as shown and described in the commonly assigned application of Pitts and Steele, entitled, Automatic Supply Package Indexing Mechanism for Winding Machines, and for a more complete understanding of the construction of the slub catcher, as well as of the forward section of the winding machine, reference may be made to that application. For present purposes, it is merely enough to know that the movement of lever 252 to the position shown in FIG. 5 is effective to operate a knife which cuts or otherwise interrupts the fiow of yarn to the winding section of the machine.

Adjacent frame side 23 and in front of the entire frame, in a position readily accessible to the machine attendant, is a manually operated starting lever 280 constructed integrally with, or otherwise connected to, shaft 250, whereby that shaft will be rocked in a counterclockwise direction (in FIG. 1) when lever 289 is pulled downwardly. Arm 280 and shaft 256 are biased in the opposite direction by means of a torsion spring 282 (see FIG. 3) encircling the shaft adjacent frame side 22 and anchored at one end in a collar 284 fast on shaft 250, and at the other in frame side 22. On the end of shaft 250 outside frame side 22 is aflixed a crank 286 extending generally vertically and terminating at its upper end above the top of side 22. A pin 288 is aflixe-d on the upper end of crank 286 for engagement with an elongated slot cut in the front end of a connecting link 292. Link 292 extends above frame side 22 from a point at its front end to a point adjacent its rear end, being offset laterally, as at 294, to clear other members, in particular support arm 56 for braking member B, and is pivoted at its rear end to the lower end of the rearmost arm 204 of sizing latch 196.

It will be seen that as starting lever 280 is rocked downwardly to re-start the machine, as when a completed package has been removed and a fresh tube placed on the winding mandrel, counterclockwise rotation of crank 86, after pin 288 has reached the forward limit of slot 290, will rock sizing latch 196 clockwise to disengage shoulder 206 on the sizing latch tail from the rear end of lug 185, permitting package extension arm 28 to be lowered into winding position with the package tube in peripheral contact wit-h driving roll D, and will at the same time pull \main package arm 38 forwardly to bring pin 50 into engagement with shoulder 48 on the upwardly biased end of main package positioning latch 44 to lock the main package arm in normal Winding position. The presence of the lost motion connection between crank 286 and connecting link 292 allows main package arm 38 to move freely to its various positions without affecting crank 286. Manipulation of starting lever 280 during re-starting of the machine performs various additional functions in connection with components not shown and described here, knowledge of which may be derived from the aforementioned Goodhue et al. patent.

A further point of interrelationship between the improvements of this invention and the Goodhue et al. patent concerns an L-shaped lever 296 pivoted on a stud 298 and seen in FIGS. 4 and 5. This lever forms a part "of the so-called memory unit of the machine fully described and claimed in that patent, which unit functions automatically to repeat the end-finding cycle once in the event the end is not found on the first attempt and then haltthe machine should the second attempt fail also. In order to assure that this lever remains in proper position during operation of the end-severing means so as not to give a false indication at a later time, it is extended downwardly as at 299 and provided with a laterally bent lug 300 on extension 299. Hence, as pendant 238 is pulled rearwardly by operating link 234, it will engage lug 300 to rock lever 296 counterclockwise (in FIGS. 4 and 5). When the pendent and operating lever return to normal running position, lever 296 will return also and will be ready for the next end-finding cycle.

One advantage not previously alluded to, in divorcing the means for positioning the main package arm in normal running position from the cam for controlling the movement of that arm during an end-finding cycle is that this arrangement enables one to vary the delay between the actuation of the thread breakage lever and the beginning of the end-finding cycle by replacing drive-plate 140, as shown, with a similar plate having a diiferent spatial relationship between the notches and pins thereon, by virtue of the fact that the positioning of the main package supporting arm takes place immediately and independently of the end-finding cycle. Obviously, if each notch on plate 140 were spaced farther behind the corresponding pin a longer interval will exist between the actuation of the latch lever by the breakage-lever pendant and the coupling of the drive plate and actuator disc to 'start the cam cycle. In this way, the timingof the endfinding cycle can be retarded or advanced as desired.

As an explanation of the operation of each of the major mechanisms involved in the present invention was provided in connection with the description of these mechanisms. Further discussion of the operation thereof is considered unnecessary. However, from what has been stated, it will be seen that the invention achieves each of the objectives set forth in the introduction to the specification and constitutes a highly satisfactory solution to the postulated diificulties inherent in the control section of the winding machine disclosed in Goodhue et a1. 2,764,362.

The precise embodiment described and illustrated here is provided for purposes of example only, as the construction and cooperation of various elements is obviously subject to modification and variation without departing from the spirit of the invention. Accordingly, the scope of the invention should be measured by the appended claims rather than by the details of the exemplary embodiment.

Having thus described my invention, that which is claimed is:

1. In a winding machine for winding yarn upon a rotating package wherein the package is rotated by frictional contact with a drive roll and is supported on an arm mounted on a frame :for movement to and from an operative position with said package contacting said roll, said arm being biased to move away from said operative position to separate said package from said roll, the improvement comprising latch means for said arm, said latch means comprising a movable latch element and a surface of abutment for said latch element, one of said element and surface being carried on said frame and the other on said arm, said element engaging said surface to maintain the arm in said operative position against said bias during normal winding, means for detecting the presence of yarn wound upon said drive roll instead of said package, means for detecting an interruption in the flow of yarn to said package, means for detecting the completion of a package, and means responsive to each of said detecting means for moving said latch element out of engagement with said surface whereby the arm is free to move away from said operative position under the influence of said bias and thereby separate said package from said driving roll.

2. A winding machine as in claim 1 including means for severing the yarn traveling to said package, means normally operative to connect said severing means to said arm to actuate said severing means when said arm moves away from said operative position to move said package away from said roll, and means for rendering said severing means inoperative in response to the operation of said second mentioned detecting means whereby said severing means is operated by movement of said arm as a result of yarn wound on the roll and completion of a package but not by movement of the arm as a result of interruption of yarn flow.

3. A winding machine as in claim 1, wherein said means for detecting the presence of yarn wound on said driving roll includes an elongated member mounted in spaced parallel relationship to the axis of said roll and in close proximity to the roll periphery, whereby said member will be contacted and moved by yarn wound on said roll, and said mean-s for moving said latch element is a connection between said elongated member and said element whereby movement of the member releases the element.

4. A winding machine as in claim 1 including a cam follower connected to said arm for unitary movement therewith; a cyclically rotatable cam cooperating with said follower for controlling the pivotal movement of said arm and the package supported thereby in a cycle from said operative position to an intermediate position spaced from said operative position, then to a remote position spaced farther from said operative position, next back to said intermediate position, and finally to said operative position, said cam having a maximum radius portion corresponding to said operative position, intermediate radius portions on either side of said maximum radius portion corresponding to said intermediate position, and a minimum radius position corresponding to said remote position, all of said portions being contacted by said follower as the cam rotates and serving tomove the follower accordingly; means responsive to detection of a yarn interruption by the corresponding detection means for initiating rotation of said earn coincidentally with the disengagement of said latch means to permit said arm to pivot and for rotating the cam to move said arm and package through said cycle; means operative while said maximum radius cam portion returns to a position contacting said follower to re-engage said latching means with said arm, whereupon said arm and follower are held in operative position; said cam rotat ing means being operative to continue cam rotation until the maximum radius position has passed out of contact with the follower, and means then effective to halt rotation of the cam so that an intermediate radius portion is in position to be contacted by said follower upon pivotal movement of said arm; whereby when said latching means is next dis-engaged in response to any detecting means, said follower immediately moves intocontact with said intermediate radius portion as said arm and package pivot due to said bias, bringing said arm and package to intermediate position. I

5. A winding machine as in claim 4 including means adapted to contact said package when in said remote position to rotate said package in a direction reverse to that of normal winding.

6. A winding machine as in claim 4 wherein said means for initiating rotation of said cam includes means for dis-engaging said cam rotation halting means, said last-named means being controlled by said yarn interception detecting means, and means connecting said lastnamed means to said latch-means to disengage the latter substantially simultaneously with the disengagement of the cam-halting means.

7. A winding machine as in claim 1 wherein said package supporting arm is articulated intermediate its ends and includes a main supporting portion and a package carrying extension, said main supporting portion being engaged by said latch means during normal winding and maintained in operative position with the package contacting the drive roll, said extension being adapted to pivot about the axis of articulation to permit said package to grow; said package completion detection means comprises a sizing plate connected to said extension for pivotal movement therewith, a member disposed adjacent said sizing plate for movement from and to a retracted position to and from a projected position, said member being maintained in said retracted position during normal Winding, and means provided at a fixed point on said sizing plate for engaging and moving said member to said projected position when said arm and said plate pivot an extent corresponding to ultimate package size; and said means for dis-engaging said latch mean in response to said package completion means is operated by the movement of said member to projected position.

8. A winding machine as in claim 7 wherein said sizing plate is adapted to be adjusted relative to said exten sion in advance of the winding operation to vary the extent of pivotal movement of said arm and plate required to bring said means on said sizing lever into engagement with said member to move the same to projected position, whereby the ultimate package size at which the latch means is dis-engaged may be varied.

9. A winding machine as in claim 7 wherein said means for dis-engaging said latch means comprises a rigid extension on said member, said extension contacting said latch means as said member moves to projected position and dis-engaging said latch means.

10. A winding machine as in claim 7 wherein said member is pivoted on said package supporting arm for bodily movement therewith, said machine including a fixed detent located adjacent a predetermined point on the path of said member when moving bodily with said arm, said member having means for engaging said detent when in projected position upon bodily movement thereof with said arm, engagement of said detent and engaging means halting further pivotal movement of said arm and package away from said drive roll, said predetermined point being so selected that the package when so halted is in a position of easy accessibility adjacent said operative position but with the package disengaged from said driving roll.

11. A winding machine for winding yarn upon a rotating package wherein the package is rotated by frictional contact with a drive roll, said machine comprising a frame, an arm supporting said package from one end thereof, said arm being pivoted in said frame at its other end for movement of the package from and to an operative position contacting said roll, said arm being biased to move said package away from said roll, a latch lever pivoted to said frame, said lever having an abutment thereon spaced from its pivot axis, a detent on said arm adapted to be engaged by said abutment to latch said arm against pivotal movement due to said bias while said package is in operative position during normal winding, means for detecting the occurrence of at least one abnormal condition during winding, and means operative in response to said detecting means to pivot said latch lever to disengage said abutment from said detent, whereby said arm pivots due to said bias to remove said package from said roll and halt the winding operation in the event such abnormal condition occurs.

12. A winding machine as in claim 11 wherein said detecting means is adapted to move when said abnormal condition occurs, and said means operative in response to said detecting means comprises mechanical means for transmitting the movement of said detecting means of said latch lever to pivot the same.

13. A Winding machine as in claim 11 including separate means for detecting an interruption in the supply of yarn, an accumulation of yarn upon said drive roll, and the attainment of ultimate package size, said means operative to pivot said latch means being responsive to each of said detecting means.

14. A winding machine as in claim 13 wherein each of said detecting means is adapted to move upon the occurrence of the condition detected thereby, and including a separate mechanical means associated with each detecting means for transmitting the movement of said detecting means to said latch lever to pivot the same.

15. A winding machine as in claim 14 wherein the yarn accumulation detection means comprises an elongated bar disposed in closely adjacent parallel relationship to the roll surface and said mechanical means associated therewith comprises a rigid connection between said rod and said latch lever, said connection constituting the support for said bar, whereby yarn accumulating upon said roll forces said bar away from the roll surface, such movement of the bar being transmitted through said connection, causing said latch lever to pivot.

16. A winding machine as in claim 14 wherein the yarn interruption detection means comprises a feeler pivotally mounted on said frame for engagement with the moving strand of yarn in advance of said package, means biasing the feeler for pivotal movement in the absence of said strand thereat; and said mechanical means comprises a rockable mechanical linkage connected at one end to said latch lever so that rocking of the linkage pivots said latch lever, said linkage terminating in a free end at the other end, a positively-driven impulse element periodically passing in close proximity to but out of contact with said free end, and a pendant movable upon pivotal movement of said yarn-engaging feeler to a position interposed between said impulse element and said free end, said pendant having a dimension exceeding the clearance between the impulse element and free end, whereby said linkage is rocked by the movement of the impulse member transmitted through said pendant to the free end thereof, pivoting said latch lever.

17. A winding machine as in claim 14 wherein said package supporting arm is articulated intermediate its ends and includes a main supporting leg provided with said abutment and an extension carrying said package at its free end, said extension being adapted to pivot about the axis of articulation to permit the package togrow while said main leg is held against movement; said package size detecting means comprises a sizing plate connected to said extension for pivotal movement therewith, said plate having an elongated abutment terminating at a predetermined point selected in accordance with the desired ultimate package size, a sizing latch rockably disposed adjacent said abutment, means biasing said sizing latch against said abutment, said sizing latch being restrained against rocking movement by said abutment as said sizing plate and extension pivot until the abutment termination is reached coincidentally with the attainment of ultimate package size, whereupon said sizing latch undergoes rocking movement under the infiuence of said biasing means; and said mechanical means associated with said package size detecting means comprises a rigid extension on said sizing latch, extending to said latch lever, said extension being held away from said latch lever while the sizing latch is restrained by the sizing plate abutment and being impinged against said latch lever when said sizing latch rocks so as to pivot said latch lever.

18. A winding machine as in claim 17 wherein said sizing latch includes a detent adapted for engaging with the termination of the sizing plate abutment when said sizing latch rocks, engagement of the same locking said supporting arm extension against pivotal movement relative to said main supporting leg in the direction of said drive roll.

19. A winding machine as in claim 17 wherein said sizing latch is pivoted on said main supporting leg for bodily movement with said leg as the latter pivots under said bias when said latch lever is pivoted to disengage the latch lever abutment from said detent on said main leg, said latch lever is provided with a further abutment in the path of said sizing latch during bodily movement thereof with said leg and said sizing latch extension is formed with a detent to engage said further abutment as said sizing latch moves along said path when said sizing latch rocks to impinge said extension on the latch lever and said main leg pivots, engagement of the extension detent and further abutment stopping further pivotal movement of said main leg with said package in a predetermined position out of contact with said driving roll.

References Cited in the tile of this patent UNITED STATES PATENTS 

1. IN A WINDING MACHINE FOR WINDING YARN UPON A ROTATING PACKAGE WHEREIN THE PACKAGE IS ROTATED BY FRICTIONAL CONTACT WITH A DRIVE ROLL AND IS SUPPORTED ON AN ARM MOUNTED ON A FRAME FOR MOVEMENT TO AND FROM AN OPERATIVE POSITION WITH SAID PACKAGE CONTACTING SAID ROLL, SAID ARM BEING BIASED TO MOVE AWAY FROM SAID OPERATIVE POSITION TO SEPARATE SAID PACKAGE FROM SAID ROLL, THE IMPROVEMENT COMPRISNG LATCH MEANS FOR SAID ARM, SAID LATCH MEANS COMPRISING A MOVABLE LATCH ELEMENT AND A SURFACE OF ABUTMENT FOR SAID LATCH ELEMENT, ONE OF SAID ELEMENT AND SURFACE BEING CARRIED ON SAID FRAME AND THE OTHER ON SAID ARM, SAID ELEMENT ENGAGING SAID SURFACE TO MAINTAIN THE ARM IN SAID OPERATIVE POSITION AGAINST SAID BIAS DURING NORMAL WINDING, MEANS FOR DETECTING THE PRESENCE OF YARN WOUND UPON SAID DRIVE ROLL INSTEAD OF SAID PACKAGE, MEANS FOR DETECTING AN INTERRUPTION IN THE FLOW OF YARN TO SAID PACKAGE, MEANS FOR DETECTING THE COMPLETION OF A PACKAGE, AND MEANS RESPONSIVE TO EACH OF SAID DETECTING MEANS FOR MOVING SAID LATCH ELEMENT OUT OF ENGAGEMENT WITH SAID SURFACE WHEREBY THE ARM IS FREE TO MOVE AWAY FORM SAID OPERATIVE POSITION UNDER THE INFLUENCE OF SAID BIAS AND THEREBY SEPARATE SAID PACKAGE FROM SAID DRIVING ROLL. 